US3245272A - Multi-disc speed-changing unit - Google Patents

Multi-disc speed-changing unit Download PDF

Info

Publication number
US3245272A
US3245272A US200193A US20019362A US3245272A US 3245272 A US3245272 A US 3245272A US 200193 A US200193 A US 200193A US 20019362 A US20019362 A US 20019362A US 3245272 A US3245272 A US 3245272A
Authority
US
United States
Prior art keywords
driving shaft
discs
grooves
rings
speed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US200193A
Other languages
English (en)
Inventor
Flichy Jacques
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ateliers Metallurgiques de Saint Urbain SA AMSU
Original Assignee
Ateliers Metallurgiques de Saint Urbain SA AMSU
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ateliers Metallurgiques de Saint Urbain SA AMSU filed Critical Ateliers Metallurgiques de Saint Urbain SA AMSU
Application granted granted Critical
Publication of US3245272A publication Critical patent/US3245272A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H15/00—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members
    • F16H15/02—Gearings for conveying rotary motion with variable gear ratio, or for reversing rotary motion, by friction between rotary members without members having orbital motion
    • F16H15/04—Gearings providing a continuous range of gear ratios
    • F16H15/06—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B
    • F16H15/08—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface
    • F16H15/14—Gearings providing a continuous range of gear ratios in which a member A of uniform effective diameter mounted on a shaft may co-operate with different parts of a member B in which the member B is a disc with a flat or approximately flat friction surface in which the axes of the members are parallel or approximately parallel

Definitions

  • the unit comprises a driving shaft provided wit-h grooves along which are adapted to slide conical discs, the combined assembly being mounted in the interior of a driving drum which is rigidly coupled to a driven shaft and is provided with internal grooves, there being adapted to slide along said grooves, mounting rings which each have an enlarged portion formed on the inner circular portion thereof and which are interleaved between said discs, means being provided for pressing the stack of discs and rings together and :for modifying the distance between the axis of the driving shaft ,and that of the drum. Friction members are employed.
  • the dri-ving shaft and the driving drum are eccentric with respect'to each other, with the result that the displacement of the driven shaft and of the driving drum in parallel relation to the driving shaft permits the enlarged portions of the rings to penetrate between the discs on one side of the shaft and to be freed from the said discs on the other side, with the result that the driven shaft rotates at a speed which becomes progressively lower than that of the driving shaft as the enlarged portions move nearer to the driving shaft.
  • Speed-changers of this type which have been known up to the present time have the disadvantage either of only transmitting low power outputs or of being subject to rapid wear of the friction members when transmitting high power outputs.
  • the important problem which arises in the case of all these speed-changers and which has not yet been solved is the lubrication of the friction members which are not readily accessible and nevertheless call both for effective cooling as well as a system of lubrication which permits of movement of the said friction members without Wear, but also without lany substantial slipping.
  • the present invention supplies a remedy for these disadvantages by creating a speed-changing unit of the abovementioned type which is essentially characterized in that an axial passage and radial or oblique passages pass through said driving shaft, and that said radial or oblique passages open into grooves of said driving shaft, means being provided for supplying said axial passage with lubricating fluid.
  • the yfriction discs which are fitted in said grooves and the rings which are mounted on the driving drum are accordingly supplied withV oil which thus effects .at the same time both lubrication and cooling Without any loss, and overall the active surfaces of said discs and rings.
  • deflector rings which may or may not be tooth-edged, are placed between the discs for the purpose of ensuring the distribution of oil over the entire surface of each disc.
  • the tooth-edged or indented rings must preferably be flexible and made, for example, of a plastic material such as the products of polymerization of tetrailuoroethylene, for example of a material known by the trade name Teflonf
  • a further improvement provided by the present invention consists in forming oblique grooves in the bearing surfaces of the driving -rings so as to facilitate the circulation of lubricating oil, the direction of inclination of the said grooves being dependent on the direction of rotation.
  • a deflector ring which ensures 'fluid-tightness of the ends of the grooves while yfurther ensuring the lubrication of the said outer face.
  • the distribution of oil over the outer face of the inner disc is ensured by forming oblique passages which open at the extremity of lthe shaft towards the outer face of said inner disc.
  • FIG. 1 is a partial cross-section of .a speed-changing unit in accordance with the present invention.
  • FIG. 2 is a View taken in perspective of a deflector ring in accordance with the present invention.
  • FIG. 3 is a sectional view taken along the line III-III in FIGURE 1, showing the lubricant passageways between the rings and discs.
  • the speed-changing unit illustrated in FIG. 1 is essentially constituted by a driving shaft 1 provided with grooves 2 in which are adapted to move serially arranged discs 4, 5, ⁇ 6 having conical radial cross-sections of which 6 is considered to be the inner disc.
  • a driving drum 7 fitted with an annular cover 10 having an enlarged portion 13, is provided with longitudinal grooves 8 in which are engaged teeth formed at the periphery of rings 11 and 12, there being formed on the internal circular portion of each ring .an enlarged portion 14, 15.
  • the cover 10 is also provided with a similar enlargement 13 formed in the internal circular portion thereof.
  • the driving drum 7 is rigidly secured by means of bolts 16 to a flange member 17 inside which is adapted to slide the tail portion 118 of a clamping or abutting member 19 which is referred to ⁇ as .a tulip.
  • the said abutting member produces a powerful clamping action between the discs and rings by being brought to bear against these latter directly, or indirectly if an additional ring is fitted against the first disc 6.
  • the tail portion 1-8 of the abutting member 19 is mounted on the driven shaft 20 Iand is of relatively substantial length in such manner as to provide a good guiding action.
  • the ilange member 17 is provided around the driven shaft with threaded bores 21 which can be made to coincide with orifices 22 formed in a fiange 23 which forms a bearing, the two flanges being rigidly assembled together by means of bolts 24 screwed inside the bores 21.
  • the relative position of the two members 19 and 17 varies with the speed ratio, that is to say with the depth of penetration inside the member 17 of the abutting member or tulip 1-9 which moves axially with respect to the drivin-g drum 7.
  • a spring 25 which is housed between the driven shaft 20 and the tail portion 18 bears on the one hand against a shoulder of this latter and, on the other hand, against ,an annular flange of the driven shaft 20.
  • the flange member 23 is keyed on the driven shaft 20 so as to permit the driving of this latter by the drum 7.
  • FIG. l shows the system in the stepped-down condition, or low speed ratio.
  • any variation in the speed ratio requires an axial displacement of the serially arranged discs 4, 5, 6 with respect to the grooved driving shaft 1, .and similarly an axial displacement of the rings 11, 12 with respect to their driving drum 7.
  • the driving shaft 1 there is formed in the driving shaft 1 a longitudinal passage 3-2 from which lead radial passages 33, 34 which open into the grooves 2.
  • the said radial passages have preferably a fairly large diameter so as to require only a low oil pressure at the entrance of the oil piping system. 'IIhe lubrication of the discs inside the vgrooves is thus ensured by means of the oil which is supplied through the said passages.
  • the distribution of oil over the entire surface of the said discs is carried out by means of dellector rings 35, 3d.
  • a deflector ring of appropriate elongated shape which is ⁇ applied on one side .against the disc 4 and on the other side against the driving shaft 1 so as to lubricate the outer face of the outer disc 4.
  • the rings which have the shape as illustrated in FIG. 2 are preferably ⁇ indented around their outer rim at 38.
  • the rdeflector rings 35, 36, 37 are preferably formed of a llexible material, for example a material such as the products of polymerization of tetrafluoroethylene.
  • the evacuation of oil is effected through passages 39 provided at the periphery of the driving drum 7.
  • substantially radial passages through the shaft 1 which ensure the lubrication of the outer face of the inner disc 6.
  • Similar groove means is provided between the .axial surfaces of the discs 4 and 6 and the corresponding bearing surfaces of the portions 9, 13 and ⁇ 15.
  • a speed-changing unit comprising a driving shaft provided with grooves along which are adapted to slide conical discs, the combined assembly being mounted in the interior of a driving drum which is drivingly coupled to a driven shaft and is provided with internal grooves, there being adapted to slide along said grooves rings which each have an enlarged portion formed on lthe inner circular portion thereof and which are interposed between said discs, clamping means provided for pressing the stack of discs and rings together and means for modifying the distance between the axis of the drum ⁇ and the axis of the driving shaft, means defining ⁇ an axial passage and substantially radial passages communicating with said axial passage and passing through said driving shaft, said substantially radial passges opening into the grooves of said driving shaft, means provided vfor supplying said axial passage with lubricating fluid, and Ia tooth-edged dellector -ring placed between each pair of adjacent discs.
  • a speed-changing unit comprising:
  • conical disc means nonrotatably and axially slideably supported upon said driving shaft substantially concentric therewith;
  • drum means and means concentrically coupling said drum means to said driven shaft for rotational movement therewith, said disc means being disposed within said drum means;
  • ring means nonrotatably and axially slideably mounted substantially concentrically within said drum means, the inside diameter of said ring means being less than the outside diameter of said disc means and said ring means being interleaved with said disc means, said ring means having annular axial faces close to their radially inner edges engaged with the axial surfaces on said disc means;
  • actuating means for supporting said driving shaft for effecting relative movement of said driving and driven shafts, whereby to effect corresponding relative radial movement of said disc means and said ring means;
  • passage means for applying lubricating fluid to the surfaces of said disc means engaged by said faces of said ring means, whereby rotation of said driving shaft causes said lluid to move radially outwardly along said disc means and between the surfaces of said disc means and the faces of said ring means.
  • a speed-changing unit according to claim 2 wherein said grooves are formed in said faces of said rings at spaced intervals.
  • a speed-changing unit according to claim 3, wherein said grooves are inclined in the direction of rotation thereof around the axis of the driving shaft.
  • a speed-changing unit wherein said driving shaft has lengthwise groove means in the outer surface thereof and said conical disc means have integral key means slideably disposed within said groove means;
  • passage means comprises a substantially axial passageway within said driving shaft and a plurality of substantially radially extending passageways communicating between said axial passageway and said groove means.
  • a speed-changing unit comprises plural discs and the one of said discs closest to said driven shaft has one axial surface facing said driven shaft;
  • said pressure means includes an annular member axially slideably supported upon said driven shaft and having an annular edge surface engaged with said one axial surface of said one disc, and resilien'tly ilexible means connected to said driven shaft and urging said annular edge surface against said one axial surface; and
  • At least one of said substantially radial passage- Ways opens radially through said driving shaft between said one axial surface and said driven shaft.
  • a speed changing unit ineluding an axially elongated deflector ring encircling said driving shaft and located adjacent the axial surface of said disc means remote from said driven shaft.
  • a speed-changing unit in which said dee'ctor ring is exible.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • General Details Of Gearings (AREA)
US200193A 1961-06-08 1962-06-05 Multi-disc speed-changing unit Expired - Lifetime US3245272A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR864314A FR1299074A (fr) 1961-06-08 1961-06-08 Variateur de vitesses à frictions multiples

Publications (1)

Publication Number Publication Date
US3245272A true US3245272A (en) 1966-04-12

Family

ID=8756817

Family Applications (2)

Application Number Title Priority Date Filing Date
US200193A Expired - Lifetime US3245272A (en) 1961-06-08 1962-06-05 Multi-disc speed-changing unit
US414647A Expired - Lifetime US3347107A (en) 1961-06-08 1964-11-30 Devices employing a friction drive between two surfaces in a liquid medium

Family Applications After (1)

Application Number Title Priority Date Filing Date
US414647A Expired - Lifetime US3347107A (en) 1961-06-08 1964-11-30 Devices employing a friction drive between two surfaces in a liquid medium

Country Status (2)

Country Link
US (2) US3245272A (fr)
FR (1) FR1299074A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871239A (en) * 1973-08-02 1975-03-18 Twin Disc Inc Variable speed drive
US4047443A (en) * 1974-11-18 1977-09-13 Automobiles Peugeot Speed variator having friction elements
US4995279A (en) * 1987-08-25 1991-02-26 Jaguar Cars Limited Transmission systems
EP0553601A3 (en) * 1992-01-30 1993-11-18 Pietro Gilberti A stepless speed change gear

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1344350A (fr) * 1962-10-02 1963-11-29 G Societes Aries Ab Procédé de lubrification des variateurs de vitesse et variateurs en comportant l'application
SE314567B (fr) * 1963-12-02 1969-09-08 Metallurg De Saint Urbain Atel
FR2347580A1 (fr) * 1976-04-06 1977-11-04 Citroen Sa Variateur de vitesse perfectionne
GB8316026D0 (en) * 1983-06-11 1983-07-13 Lucas Ind Plc Self-energising disc brakes
FR2764656B1 (fr) * 1997-06-17 1999-07-16 Valeo Disque de friction d'embrayage pour embrayage fonctionnant a sec, plus particulierement pour vehicule automobile, ainsi qu'une couronne de frottement en materiau de friction, destinee a equiper un tel disque de friction
US6478130B2 (en) 2000-12-22 2002-11-12 Eaton Corporation Clutch friction button
CN1578890B (zh) * 2002-09-30 2010-05-26 乌尔里克·罗斯 传动机构
EP1546578B1 (fr) * 2002-09-30 2014-11-19 Rohs, Ulrich, Dr. Engrenage planetaire
DE10309062A1 (de) * 2003-03-03 2004-09-16 Bayerische Motoren Werke Ag Reibrad eines Reibradgetriebes für ein von einem Aggregate-Riementrieb einer Brennkraftmaschine gesondert angeordnetes Nebenaggregat
JP2014098436A (ja) * 2012-11-14 2014-05-29 Jtekt Corp クラッチプレート、クラッチ装置、及び駆動力伝達装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE897942C (de) * 1950-06-06 1953-11-26 Patentverwertung W Reimers G M Stufenlos regelbares Reibraedergetriebe
DE930064C (de) * 1952-07-17 1955-07-07 Daimler Benz Ag Reibungsgetriebe, insbesondere fuer Kraftfahrzeuge
US2748614A (en) * 1953-06-23 1956-06-05 Zenas V Weisel Variable speed transmission

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2775331A (en) * 1951-06-02 1956-12-25 Gen Motors Corp Clutch with coolant metering
GB787579A (en) * 1954-08-31 1957-12-11 Geoffrey Robert Greenbergh Gat Improvements in or relating to clutch plates
US3099927A (en) * 1960-09-09 1963-08-06 Ford Motor Co Infinitely variable transmission
US3202253A (en) * 1961-12-04 1965-08-24 Clark Equipment Co Clutch cooling means
US3238818A (en) * 1963-05-10 1966-03-08 Ford Motor Co Infinitely variable friction disc drive

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE897942C (de) * 1950-06-06 1953-11-26 Patentverwertung W Reimers G M Stufenlos regelbares Reibraedergetriebe
DE930064C (de) * 1952-07-17 1955-07-07 Daimler Benz Ag Reibungsgetriebe, insbesondere fuer Kraftfahrzeuge
US2748614A (en) * 1953-06-23 1956-06-05 Zenas V Weisel Variable speed transmission

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871239A (en) * 1973-08-02 1975-03-18 Twin Disc Inc Variable speed drive
US4047443A (en) * 1974-11-18 1977-09-13 Automobiles Peugeot Speed variator having friction elements
US4995279A (en) * 1987-08-25 1991-02-26 Jaguar Cars Limited Transmission systems
EP0553601A3 (en) * 1992-01-30 1993-11-18 Pietro Gilberti A stepless speed change gear

Also Published As

Publication number Publication date
US3347107A (en) 1967-10-17
FR1299074A (fr) 1962-07-20

Similar Documents

Publication Publication Date Title
US3245272A (en) Multi-disc speed-changing unit
SU1722246A3 (ru) Бесступенчато-регулируема коническа фрикционна передача
CA1083505A (fr) Soupage de decharge pour embrayage hydraulique
US4307584A (en) Resilient coupling mechanism
US3365913A (en) Rotary shaft coupling device
JPS6174971A (ja) プーリ
DE2759315C2 (de) Rotor für eine Füllgutkupplung
DE2614151C3 (de) Reibungskupplung
US1934850A (en) Clutch device with a. hydraulic servomotor
US2015212A (en) Device for the hydraulic transmission of power
US2035582A (en) Variable ratio transmission device
US2020002A (en) Packing
US2891410A (en) Speed varying device
US3177734A (en) Variable-speed transmissions utilizing belts and pulleys
US2681578A (en) Two-speed drive
US3386300A (en) Variable speed sheave
US4050557A (en) Two-speed transmission having enclosed flywheel
US1268632A (en) Flexible coupling.
US3486387A (en) Vibrating mechanism
US905756A (en) Sheave.
US3407627A (en) Elastic coupling for high dynamic stresses
JPH0469412A (ja) 変速機用ドラム
US1971955A (en) Reversing gear and clutch mechanism
US2825234A (en) Multiple arrangement for frictional power transmission
US2756856A (en) Centrifugal clutches